CN103867656A - Transmission with two clutches and two intermediate shafts - Google Patents
Transmission with two clutches and two intermediate shafts Download PDFInfo
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- CN103867656A CN103867656A CN201410094333.5A CN201410094333A CN103867656A CN 103867656 A CN103867656 A CN 103867656A CN 201410094333 A CN201410094333 A CN 201410094333A CN 103867656 A CN103867656 A CN 103867656A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/12—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts with means for synchronisation not incorporated in the clutches
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
- F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
- F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
- F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
- F16H2003/0936—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts with multiple countershafts comprising only two idle gears and one gear fixed to the countershaft
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention relates to a transmission with two clutches and two intermediate shafts. The transmission comprises the two clutches, a solid input shaft, a hollow input shaft, the two intermediate shafts and an output shaft, wherein the left ends of the coaxially designed solid input shaft and hollow input shaft are respectively connected with the two clutches, the right ends of the solid input shaft and the hollow input shaft are respectively connected with normally engaged gears in the transmission, the transmission has twelve speed states comprising five low-speed forward gears, five high-speed forward gears and two reverse gears, driving gears connected with the solid input shaft are simultaneously engaged with corresponding driven gears on the two intermediate shafts with relatively small transmission degree for forming the five high-speed forward gears and a high-speed reverse gear of the transmission, and driving gears connected with the hollow input shaft are simultaneously engaged with corresponding driven gears on the two intermediate shafts with relatively large transmission degree for forming the five speed-speed forward gears and a low-speed reverse gear of the transmission. An auxiliary box of the existing transmission with two intermediate shafts is omitted, the structure of the transmission is more compact, the axial size of the whole transmission is reduced, and the weight of the main body of the transmission is reduced by 5%-20%.
Description
Technical field
The invention belongs to automotive transmission technical field, be specifically related to a kind of speed changer for heavy-duty car.
Background technique
Heavy-duty car own wt is very large, and Deadweight cargo capacity requires larger, and working environment is often all very complicated, severe.In the development of heavy-duty car high-power, in order to meet better and the mating and the requirement such as power performance and climbing of car load of motor, constantly reduce oil consumption, raise the efficiency, its speed changer is also towards many gears, large speed ratio, little differential future development.Research shows, expands transmission ratio scope and can make heavy-duty car have good power character, Economy and travelling comfort with increase transmission gear figure place.At present, the domestic twin countershaft transmission that uses more, this speed changer is divided into main-gear box, two parts of auxiliary transmission, main-gear box part adopts two jack shaft modes to reach the object of power dividing, and auxiliary transmission part exists two kinds of shunting modes: a kind of is to adopt the two jack shaft modes identical with main-gear box; Another kind is to adopt planetary gear train structure.Although twin countershaft transmission has been widely used in heavy-duty car field, still there is following point in it: 1. speed changer structure complexity.Existing twin countershaft transmission is divided into two parts of major and minor gearbox, realize gear number at double, but odd-side structure is very complicated by the synchronizer of odd-side, so that the housing structure of speed changer entirety becomes is also very complicated, and the processing technology more complicated of casing.2. assembly technology is very complicated.The structure of the major and minor case of existing twin countershaft transmission has been used multiple shafting structures, and the labyrinth of casing, makes the assembly technology of speed changer very complicated.3. axial dimension, volume and quality are larger.The axial dimension of existing twin countershaft transmission entirety is larger, and shared volume is large, and quality is also larger.
Summary of the invention
The problem existing in order to solve the existing speed changer for heavy-duty car, the invention provides the speed changer with the two jack shafts of two clutches.
Concrete technical solution is as follows:
The speed changer with the two jack shafts of two clutches comprises primary input axle 1, output shaft 6, the first jack shaft 5, the second jack shaft 7 and double clutch 2, on described output shaft 6, empty set is provided with five gear driven gears 12, four gear driven gears 14, three gear driven gears 17, two gear driven gears 20, gear driven gear 21 and the driven gear 24 that reverses gear successively, wherein the output shaft 6 between five gear driven gears 12 and four gear driven gears 14 is provided with the 3rd synchronizer 33, three gear driven gears 17 and the output shaft 6 of two gears between driven gears 20 are provided with the second synchronizer 30, one gear driven gears 21 and the output shaft 6 that reverses gear between driven gear 24 is provided with the first synchronizer 25, on described the first jack shaft 5, be fixed with successively the first low speed driven gear 10, the first high speed driven gear the 11, the 1 gear driving gear the 13, the 1 gear driving gear the 15, the 1 gear driving gear the 16, the 1 gear driving gear the 18, the 1 gear driving gear 19 and first driving gear 22 that reverses gear, on described the second jack shaft 7, be fixed with successively the second low speed driven gear 36, the second high speed driven gear the 35, the 25 gear driving gear the 34, the 24 gear driving gear the 32, the 23 gear driving gear the 31, the 22 gear driving gear the 29, the 21 gear driving gear 28 and second driving gear 27 that reverses gear, wherein the one or five gear driving gear 13, the two or five gear driving gear 34 respectively with five gear driven gears 12 engage, the one or four gear driving gear 15, the two or four gear driving gear 32 respectively with four gear driven gears 14 engage, the one or three gear driving gear 16, the two or three gear driving gear 31 respectively with three gear driven gears 17 engage, the one or two gear driving gear 18, the two or two gear driving gear 29 respectively with two gear driven gears 20 engage, the one one gear driving gear 19, the 21 gear driving gear 28 respectively with one gear driven gears 21 engage, first driving gear 22 that reverses gear engages by the first reverse gear idle pulley 23 and driven gear 24 that reverses gear, second driving gear 27 that reverses gear engages by the second reverse gear idle pulley 26 and driven gear 24 that reverses gear,
The output terminal of described primary input axle 1 is connecting the sheet support arm of double clutch 2, and the opposite side of solid input shaft 3 is provided with high gear 9, and described high gear 9 respectively with the first high speed driven gears 11, the second high speed driven gear 35 engage; Solid input shaft 3 overhead are arranged with hollow input shaft 4; The sheet inner support of one end of described hollow input shaft 4 and double clutch 2 is connected, and the other end is provided with low speed gear 8, and described low speed gear 8 respectively with the first low speed driven gears 10, the second low speed driven gear 36 engage;
Described solid input shaft 3, hollow input shaft 4 and output shaft 6 are coaxial, and corresponding moving cooperation of the inner of the other end of solid input shaft 3 and output shaft 6.
The other end of the solid input shaft 3 corresponding with the inner of output shaft 6 is sleeve pipe, and the inner of output shaft 6 is plugged in the sleeve pipe of solid input shaft 3.
Between described the 3rd synchronizer 33, the second synchronizer 30, the first synchronizer 25 and output shaft 6, being involute splines connects.
Compared with prior art, useful technique effect of the present invention embodies in the following areas:
1. described in, speed changer has continued current twin countershaft transmission in many-sided advantages such as bearing capacity, power dividing and many gears.When double clutch 2 is worked by the different clutches of selection, to input different initial velocity ratios to speed changer, the difference of initial velocity ratio is: the velocity ratio that high gear 9 and the first high speed driven gear 11 and the second high speed driven gear 35 engage is simultaneously top gear district; The velocity ratio that low speed gear 8 and the first low speed driven gear 10, the second low speed driven gear 36 engage is simultaneously bottom gear district.High speed and low speed Liang Gedang district share the main driven gear of the each gear of speed changer.Adopt double clutch 2 to control respectively bottom gear district and the top gear district of described speed changer, i.e. the switching of bottom gear and top gear is to realize by the switching of double clutch 2;
2. the output terminal of the output shaft 6 of speed changer directly outputs to ransaxle by transmission shaft, save the auxiliary transmission structure of current twin countershaft transmission, shorten the axial dimension of speed changer entirety, simplify the housing structure of current speed changer complexity, bring good technology capability to mission case, comprehensively reduce costs.Can realize speed changer main body loss of weight 5%-20%;
3. simplified the labyrinth of current twin countershaft transmission casing, optimized the assembly process process of speed changer, described speed changer structure is simple, compact, is convenient to assembling and maintenance.Can shorten installation time 10%-30%, increase work efficiency.
Accompanying drawing explanation
Fig. 1 is structural representation of the present invention.
Fig. 2 is that the present invention one keeps off power bang path schematic diagram.
Fig. 3 is that the present invention six keeps off power bang path schematic diagram.
Fig. 4 is the low speed of the present invention power bang path schematic diagram that reverses gear.
Fig. 5 is the present invention's power bang path schematic diagram that reverses gear at a high speed.
Sequence number in upper figure: primary input axle 1, double clutch 2, solid input shaft 3, hollow input shaft 4, the first jack shaft 5, output shaft 6, the second jack shaft 7, low speed gear 8, high gear 9, the first low speed driven gear 10, the first high speed driven gear 11, five gear driven gears 12, the one or five gear driving gear 13, four gear driven gears 14, the one or four gear driving gear 15, the one or three gear driving gear 16, three gear driven gears 17, the one or two gear driving gear 18, the one one gear driving gear 19, two gear driven gears 20, one gear driven gear 21, first driving gear 22 that reverses gear, first idle pulley 23 that reverses gear, driven gear 24 reverses gear, the first synchronizer 25, second idle pulley 26 that reverses gear, second driving gear 27 that reverses gear, the 21 gear driving gear 28, the two or two gear driving gear 29, the second synchronizer 30, the two or three gear driving gear 31, the two or four gear driving gear 32, the 3rd synchronizer 33, the two or five gear driving gear 34, the second high speed driven gear 35, the second low speed driven gear 36.
Embodiment
Below in conjunction with accompanying drawing, by embodiment, the present invention is further described.
Referring to Fig. 1, the speed changer with the two jack shafts of two clutches comprises primary input axle 1, output shaft 6, the first jack shaft 5, the second jack shaft 7 and double clutch 2, on described output shaft 6, empty set is provided with five gear driven gears 12, four gear driven gears 14, three gear driven gears 17, two gear driven gears 20, gear driven gear 21 and the driven gear 24 that reverses gear successively, wherein the output shaft 6 between five gear driven gears 12 and four gear driven gears 14 is provided with the 3rd synchronizer 33, three gear driven gears 17 and the output shaft 6 of two gears between driven gears 20 are provided with the second synchronizer 30, one gear driven gears 21 and the output shaft 6 that reverses gear between driven gear 24 is provided with the first synchronizer 25, on described the first jack shaft 5, be fixed with successively the first low speed driven gear 10, the first high speed driven gear the 11, the 1 gear driving gear the 13, the 1 gear driving gear the 15, the 1 gear driving gear the 16, the 1 gear driving gear the 18, the 1 gear driving gear 19 and first driving gear 22 that reverses gear, on described the second jack shaft 7, be fixed with successively the second low speed driven gear 36, the second high speed driven gear the 35, the 25 gear driving gear the 34, the 24 gear driving gear the 32, the 23 gear driving gear the 31, the 22 gear driving gear the 29, the 21 gear driving gear 28 and second driving gear 27 that reverses gear, wherein the one or five gear driving gear 13, the two or five gear driving gear 34 respectively with five gear driven gears 12 engage, the one or four gear driving gear 15, the two or four gear driving gear 32 respectively with four gear driven gears 14 engage, the one or three gear driving gear 16, the two or three gear driving gear 31 respectively with three gear driven gears 17 engage, the one or two gear driving gear 18, the two or two gear driving gear 29 respectively with two gear driven gears 20 engage, the one one gear driving gear 19, the 21 gear driving gear 28 respectively with one gear driven gears 21 engage, first driving gear 22 that reverses gear engages by the first reverse gear idle pulley 23 and driven gear 24 that reverses gear, second driving gear 27 that reverses gear engages by the second reverse gear idle pulley 26 and driven gear 24 that reverses gear.
The output terminal of primary input axle 1 is connecting the sheet support arm of double clutch 2, and the opposite side of solid input shaft 3 is provided with high gear 9, and described high gear 9 respectively with the first high speed driven gears 11, the second high speed driven gear 35 engage; Solid input shaft 3 overhead are arranged with hollow input shaft 4; The sheet inner support of one end of described hollow input shaft 4 and double clutch 2 is connected, and the other end is provided with low speed gear 8, and described low speed gear 8 respectively with the first low speed driven gears 10, the second low speed driven gear 36 engage;
Described solid input shaft 3, hollow input shaft 4 and output shaft 6 are coaxial, and corresponding moving cooperation of the inner of the other end of solid input shaft 3 and output shaft 6, the other end of the solid input shaft 3 corresponding with the inner of output shaft 6 is sleeve pipe, and the inner of output shaft 6 is plugged in the sleeve pipe of solid input shaft 3.
Between the 3rd synchronizer 33, the second synchronizer 30, the first synchronizer 25 and output shaft 6, being involute splines connects.
Working principle of the present invention is described as follows:
Referring to Fig. 2, one gear power transmission path: power is inputted from primary input axle (1), after low speed gear (8), be divided into two power streams from the first low speed driven gear (10) and the second low speed driven gear (36) respectively, to gear driven gear (21) interflow until output.Specifically be divided into:
Article 1, power bang path: power → primary input axle (1) → double clutch (2) → hollow input shaft (4) → low speed gear (8) → first low speed driven gear (10) → first jack shaft (5) → the 1 gear driving gear (19) → gear driven gear (21) → first synchronizer (25) → output shaft (6);
Article 2 power bang path: power → primary input axle (1) → double clutch (2) → hollow input shaft (4) → low speed gear (8) → second low speed driven gear (36) → second jack shaft (7) → the 21 gear driving gear (28) → gear driven gear (21) → first synchronizer (25) → output shaft (6).
Referring to Fig. 3, six gear power transmission paths: power is inputted from primary input axle (1), after high gear (9), be divided into two power streams from the first high speed driven gear (11) and the second high speed driven gear (35) respectively, to gear driven gear (21) interflow until output.Specifically be divided into:
Article 1, power bang path: power → primary input axle (1) → double clutch (2) → solid input shaft (3) → high gear (9) → first high speed driven gear (11) → first jack shaft (5) → the 1 gear driving gear (19) → gear driven gear (21) → first synchronizer (25) → output shaft (6);
Article 2 power bang path: power → primary input axle (1) → double clutch (2) → solid input shaft (3) → high gear (9) → second high speed driven gear (35) → second jack shaft (7) → the 21 gear driving gear (28) → gear driven gear (21) → first synchronizer (25) → output shaft (6).
Referring to Fig. 4, the low speed power transmission path of reversing gear: power is inputted from primary input axle (1), after low speed gear (8), be divided into two power streams from the first low speed driven gear (10) and the second low speed driven gear (36) respectively, to the follower that reverses gear (24) interflow until output.Specifically be divided into:
Article 1, power bang path: power → primary input axle (1) → double clutch (2) → hollow input shaft (4) → low speed gear (8) → first low speed driven gear (10) → first jack shaft (5) → first driving gear (22) → first idle pulley (the 23) → driven gear that reverses gear (24) → first synchronizer (the 25) → output shaft (6) that reverses gear that reverses gear;
Article 2 power bang path: power → primary input axle (1) → double clutch (2) → hollow input shaft (4) → low speed gear (8) → second low speed driven gear (36) → second jack shaft (7) → second driving gear (27) → second idle pulley (the 26) → driven gear that reverses gear (24) → first synchronizer (the 25) → output shaft (6) that reverses gear that reverses gear.
Referring to Fig. 5, the power transmission path of reversing gear at a high speed: power is inputted from primary input axle (1), after high gear (9), be divided into two power streams from the first high speed driven gear (11) and the second high speed driven gear (35) respectively, to the follower that reverses gear (24) interflow until output.Specifically be divided into:
Article 1, power bang path: power → primary input axle (1) → double clutch (2) → solid input shaft (3) → high gear (9) → first high speed driven gear (11) → first jack shaft (5) → first driving gear (22) → first idle pulley (the 23) → driven gear that reverses gear (24) → first synchronizer (the 25) → output shaft (6) that reverses gear that reverses gear;
Article 2 power bang path: power → primary input axle (1) → double clutch (2) → solid input shaft (3) → high gear (9) → second high speed driven gear (35) → second jack shaft (7) → second driving gear (27) → second idle pulley (the 26) → driven gear that reverses gear (24) → first synchronizer (the 25) → output shaft (6) that reverses gear that reverses gear.
Claims (3)
1. the speed changer with the two jack shafts of two clutches, comprises primary input axle (1), output shaft (6), the first jack shaft (5), the second jack shaft (7) and double clutch (2), on described output shaft (6), empty set is provided with five gear driven gears (12) successively, four gear driven gears (14), three gear driven gears (17), two gear driven gears (20), one gear driven gear (21) and the driven gear that reverses gear (24), wherein the output shaft (6) between five gear driven gears (12) and four gear driven gears (14) is provided with the 3rd synchronizer (33), output shaft (6) between three gear driven gears (17) and two gear driven gears (20) is provided with the second synchronizer (30), output shaft (6) between one gear driven gear (21) and the driven gear that reverses gear (24) is provided with the first synchronizer (25), on described the first jack shaft (5), be fixed with successively the first low speed driven gear (10), the first high speed driven gear (11), the one or five gear driving gear (13), the one or four gear driving gear (15), the one or three gear driving gear (16), the one or two gear driving gear (18), the one one gear driving gear (19) and first driving gear (22) that reverses gear, on described the second jack shaft (7), be fixed with successively the second low speed driven gear (36), the second high speed driven gear (35), the two or five gear driving gear (34), the two or four gear driving gear (32), the two or three gear driving gear (31), the two or two gear driving gear (29), the 21 gear driving gear (28) and second driving gear (27) that reverses gear, wherein the one or five gear driving gear (13), the two or five gear driving gear (34) respectively with five gear driven gear (12) engagements, the one or four gear driving gear (15), the two or four gear driving gear (32) respectively with four gear driven gear (14) engagements, the one or three gear driving gear (16), the two or three gear driving gear (31) respectively with three gear driven gear (17) engagements, the one or two gear driving gear (18), the two or two gear driving gear (29) respectively with two gear driven gear (20) engagements, the one one gear driving gear (19), the 21 gear driving gear (28) respectively with one gear driven gear (21) engagement, first reverses gear driving gear (22) by first idle pulley (23) and the driven gear that reverses gear (24) engagement of reversing gear, second reverses gear driving gear (27) by second idle pulley (26) and the driven gear that reverses gear (24) engagement of reversing gear, it is characterized in that: the output terminal of described primary input axle (1) is connecting the sheet support arm of double clutch (2), the opposite side of solid input shaft (3) is provided with high gear (9), described high gear (9) respectively with the first high speed driven gear (11), the second high speed driven gear (35) engagement, solid input shaft (3) overhead is arranged with hollow input shaft (4), one end of described hollow input shaft (4) is connected with the sheet inner support of double clutch (2), and the other end is provided with low speed gear (8), described low speed gear (8) respectively with the first low speed driven gear (10), the second low speed driven gear (36) engagement, described solid input shaft (3), hollow input shaft (4) and output shaft (6) are coaxial, and corresponding moving cooperation of the inner of the other end of solid input shaft (3) and output shaft (6).
2. the speed changer with the two jack shafts of two clutches according to claim 1, it is characterized in that: the other end of the solid input shaft (3) corresponding with the inner of output shaft (6) is sleeve pipe, and the inner of output shaft (6) is plugged in the sleeve pipe of solid input shaft (3).
3. the speed changer with the two jack shafts of two clutches according to claim 1, is characterized in that: between described the 3rd synchronizer (33), the second synchronizer (30), the first synchronizer (25) and output shaft (6), be involute splines and connect.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410094333.5A CN103867656B (en) | 2014-03-14 | 2014-03-14 | There is the variator of the double jackshaft of double clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410094333.5A CN103867656B (en) | 2014-03-14 | 2014-03-14 | There is the variator of the double jackshaft of double clutch |
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| Publication Number | Publication Date |
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| CN103867656A true CN103867656A (en) | 2014-06-18 |
| CN103867656B CN103867656B (en) | 2016-08-03 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410094333.5A Expired - Fee Related CN103867656B (en) | 2014-03-14 | 2014-03-14 | There is the variator of the double jackshaft of double clutch |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106715965A (en) * | 2014-11-25 | 2017-05-24 | 宝马股份公司 | Manual transmission unit with traction gear |
| CN106715963A (en) * | 2014-11-25 | 2017-05-24 | 宝马股份公司 | Transmission unit having compact structure |
| CN109312826A (en) * | 2016-06-15 | 2019-02-05 | 舍弗勒技术股份两合公司 | Vehicle transmission |
| CN112984056A (en) * | 2021-02-26 | 2021-06-18 | 淮阴工学院 | Six grades of AMT speed change systems of diaxon |
| CN115949708A (en) * | 2022-12-28 | 2023-04-11 | 江苏新能源汽车研究院有限公司 | Three-gear speed change system and driving system of heavy new energy automobile and working method of three-gear speed change system |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0321873A2 (en) * | 1987-12-19 | 1989-06-28 | GETRAG Getriebe- und Zahnradfabrik Hermann Hagenmeyer GmbH & Cie | Dual clutch transmission and its adjustment method |
| CN1062783A (en) * | 1990-12-24 | 1992-07-15 | 易通公司 | The sel-energizing synchronizer of the balance multi-gear transmission device gearshift time and the application of force |
| US20070289399A1 (en) * | 2006-06-16 | 2007-12-20 | Aisin Ai Co., Ltd. | Dual clutch transmission apparatus with parking lock function |
| CN101691885A (en) * | 2008-04-02 | 2010-04-07 | 通用汽车环球科技运作公司 | Multi-speed double-clutch variable-speed device with middle shaft transmission device |
| CN101713459A (en) * | 2009-08-11 | 2010-05-26 | 浙江吉利汽车研究院有限公司 | Double clutch type automatic gearbox |
| DE102010011917A1 (en) * | 2010-03-18 | 2011-09-22 | Daimler Ag | Motor vehicle transmission device i.e. dual-clutch transmission device, has control and/or regulating unit to open switch units of sub-transmission, when powershift clutch unit of sub-transmission is partially closed |
| CN202579992U (en) * | 2012-05-04 | 2012-12-05 | 东风汽车有限公司 | Double-intermediate-shaft double-clutch automatic gearbox structure |
| CN103124869A (en) * | 2010-09-24 | 2013-05-29 | Zf腓德烈斯哈芬股份公司 | Method for adapting a characteristic curve of clutches in a partial double-clutch transmission of a motor vehicle |
| CN203743329U (en) * | 2014-03-14 | 2014-07-30 | 合肥工业大学 | Transmission provided with double clutches and double countershafts |
-
2014
- 2014-03-14 CN CN201410094333.5A patent/CN103867656B/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0321873A2 (en) * | 1987-12-19 | 1989-06-28 | GETRAG Getriebe- und Zahnradfabrik Hermann Hagenmeyer GmbH & Cie | Dual clutch transmission and its adjustment method |
| CN1062783A (en) * | 1990-12-24 | 1992-07-15 | 易通公司 | The sel-energizing synchronizer of the balance multi-gear transmission device gearshift time and the application of force |
| US20070289399A1 (en) * | 2006-06-16 | 2007-12-20 | Aisin Ai Co., Ltd. | Dual clutch transmission apparatus with parking lock function |
| CN101691885A (en) * | 2008-04-02 | 2010-04-07 | 通用汽车环球科技运作公司 | Multi-speed double-clutch variable-speed device with middle shaft transmission device |
| CN101713459A (en) * | 2009-08-11 | 2010-05-26 | 浙江吉利汽车研究院有限公司 | Double clutch type automatic gearbox |
| DE102010011917A1 (en) * | 2010-03-18 | 2011-09-22 | Daimler Ag | Motor vehicle transmission device i.e. dual-clutch transmission device, has control and/or regulating unit to open switch units of sub-transmission, when powershift clutch unit of sub-transmission is partially closed |
| CN103124869A (en) * | 2010-09-24 | 2013-05-29 | Zf腓德烈斯哈芬股份公司 | Method for adapting a characteristic curve of clutches in a partial double-clutch transmission of a motor vehicle |
| CN202579992U (en) * | 2012-05-04 | 2012-12-05 | 东风汽车有限公司 | Double-intermediate-shaft double-clutch automatic gearbox structure |
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